Gear for attaining a compensation between driving power and load.



e. vow SAALFELD. v GEARFOR ATTAINING A COMPENSATION BETWEEN DRWING POWER AND LOAD.

APPLICATION FILED MAR. 5. 1915- 1-,172,4e12; Patented Feb. 22,1916.

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G. VUN SAALFELD. GEAR FOR ATTAINING A COMPENSATION BETWEEN DRIVING POWER AND LOAD. APPLICATION FILED MAR. 5. 1915.

' 1,172,412. Patented Feb. 22,1916.-

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if 1 a 6 Z CZ 6 Z. 02* d 0 o Cl 71 0 O 0 0 iron-swarms A COMPENSATION BETWEEN, Univ-me rowan. Ann LOAD, y

' To a Zlwho m it may concern: 5 I

Be it known that I, GnoRG VON .SAAnrnLD, a citizen of the German Empire, and res1d-- enoae von sAALrE n, or MUNIcn-HARLAcHmm-emarm.

ing at .12 Ueber der Klause, Munich-Harlaching, Bavaria, German Empire, have invented a certain new and useful Improved Gear for Attaining a Compensation Between Driving Power and Load, of whichthe following isa full, clear, and exact description.

The present invention relates to a gear for attaining a compensation between driving power and load and .is especially adapted fora machine with strongly varying resistance driven I by means of a motor subject to overloading, such, for instance,

as an internal combustion motor.

In my present invention-I provide'means as an internal combustionwengine for developing the desired power, this power be ing applied through a fluid medium to a motor carrying the load, by means of a.

hydraulic pump of variable capacity. In connection with this arrangement of parts I provide means controlled by the engine speed or power, whereby there is a normal tendency to vary the capacity of the pump in accord with the speed, or power, of the engine, supplemental means being provided whereby variance in the capacity of the pump will be modified by variance of the load upon the motor to cause the pump to respond to such variance in the -load,.in a manner to prevent an additional. load upon the engine.

For carrying the invention a intoj efle ct' a finely adjustable gear of any desired kind, such, for instance, as friction wheels, ex-

panding pulleys, Newman-gears or the like,.

must be employed. By using the invention, hereafter more fully to be explained, the

number or: rotations of the driving engine 3 Wlll remain entirely 'umnfluencedljby' the" adjustment in the gear on the one hand, while on the other hand the adjusting wdevice is'- automatically adju ted for each number of. revolutions of the driving englne. tendencyot the gear to operate to. bring the capacity of the'pump into accord with the engine speed, the term capapity of the pump relating merely to the volume of the fluid maintained .in circulation during,

a given interval, or the rate of flow of this fluid. It must be understood that the ca Specification of Lettersl'atentb Application filed March 5, 1915. Serial No. 12,422.

In other" words there is a normal pacityof th e pump ordinarily varies iiiverse ratio to the'power required tocarry the load. The-normal tendency of this-arrangementwould be to maintain the pump capacity in accord with that of the engine speed, were 'it not that I provide means,

Patented-Feb. 22, i916.- I

controlled by the load conditions, whereby i the action of-the gear in controlling the capacity of the pump'is modified in a way to vary thecapacity of the pump in accord.-

.ance with the variances iii the load, with-.

out, however, having any effect upon the eng ne speed.- I

In order to render the present inventionmore easily intelligible, a form of embodiment of the subjectmatter'of invention relating. to the hydraulic transfer of, the

working capacity of an automobile. motor' to driving pump is shown in the accom-' panying drawings'in which Figure 1. is a plan View, partly in section of the preferred form of the invention.

Fig. 2 is a view of a modified construction of the mechanicalregulator, and Fig. 3-is 8'0 a detailed sectional view of thepump.

Like letters refer to like parts through out the several views; i

Referring to the accompanying drawing, and'especially to Fig.1, a is an automobile motor and b are the rear wheels ofthe automobile. z are hydraulic driving motors connected with the said rear-wheels. e is a fiy-wheel and d' are the pump cylinders arranged in thes'ame. v f are suction chan-- nels and g pressurechannels, also provided in the fiy -wheel. his a driving medium re- 'ceptacle, adjacent to .the fly-wheel and 7b a partition wall, subdividing the said receptacle it into two annular chambers k k of I which 'h serves for admitting the driving medium from the suction conduit 2" to the suction channels 7 and h for leading off the pressure liquid from the pressure -chan'-..

a transfer conduit m, having an automatically operating .valv'e Z. This check valve" Z is so set that'the' liquid in the pressure conduit is cannot ,flow to the. compensation receptacle 2', but the liquid in the suction conduit can flow from the receptacle i 1to the receptacle is, when the'motors c are f runningv at a speed greater than their normal speed with the maximumrate of 'flow motors upon the pump. To the compensation-receptacle z" a rising-tube 11 maybe attached, which permits an expansion-of the driving medium, when the temperature rises, and a compensation of a loss of liquid due to leakage.

The pistons d of the pump cylinders 03 are by means of the piston rods d connected with a guiding piece (Z Said guiding piece is mounted upon a pivot n, which is mounted on the traveler n. The said traveler is hollow and provided with inner screw thread, and is adapted to be moved in the one or other direction by a screw-spindle 0. In place of this piston-pump any other kind of pump may be employed, the stroke of which may be varied from zero to a maximum.

0 is a toothed wheel, located on the free end of the screw-spindle 0 and engaging a rack p, which is attached to a piston q the casing q of which communicates with the pressure conduit In The other end of the rack p carries a collar 79 and terminates in a rod 79 around which a helical spring 1'' is placed. This spring is seated between adjustable.

the collar 39' and a flange s of a screw' threaded sleeve 8, which is held against rotation by means of guides t or in any other suitable manner. Said sleeve may be moved axially by means of the screw-threaded spineu. In place of the helical spring any other suitable compensation means, so, for instance, a pressure air cylinder, pendulum weights or the like may be employed.

To the end of the screw-spindle u a toothed wheel a is keyed, which is embodied as stationary member of a clutch, the movv able member of which i. e. a toothed wheel '10, is movably located upon the square-part of a shaft w. The toothed wheel 4) is by means of an intermediary toothed wheel a: in engagement with a toothed wheel 3 ,while the toothed wheel 'w engages a toothed wheel z: The toothed wheels 1 and 2, formed as clutch members, are located upon sleeves y, zf, movable on the shaft 2. The sleeve y Y is acted upon by a spring 3 and possesses an annular groove '4, into' which the forked end of a two-firmed lever 5 engages, which revolves around the pivot 6, while the:other forked end ofthe said lever 5 engages an annular groove 7- of, a sleeve 8, which is slidable on the screw-spindle u.

9 is an annular groove in the sleeve 2,

'inwhich the forked end of a two armed lever 10 engages, which is pivotally located The other forked end engages an annular groove 12 of a stop 13, placed upon the pulling-rods 14 of the regulator 15 (Fig.

1), which pulling rods are at 16 pivoted to brake-valve 27, arranged in the suction-conduit i, may be operated, the said brake 26 being under the influence ofa spring 28.

The operation of the device is as follows z-Supposing the parts occupy the positions shown in-Fig. 1 no power can be transmitted by the motor through the pipes 2', 7a to the rear-wheel motor 0, as the central axis of the pivot 72, in the traveler or slide n coincides with the central axis of the shaft of the motor a and thus the pistons d of the fly-wheel pump d are in their position of rest, the compensation spring 1' being inoperative. This position is also retained when the motor is started, but is moving with a speed to be considered as a medium. speed vice is actuated, coming'to rest when the enginereaches the maximum speed, this actuation of said regulator varying the position of the pivot n to make the pump operative.

With the actuation of said regulator, the

spring r is compressed, the actuation of the pump resulting in such a movement of the piston q as to control said spring in a manner to insure a capacity of the pump equal to the requirements of the load upon the motor 0. The spring r is compressed for an amount, .so that its tension corresponds to the pressure exerted upon the piston q, i. e. the pressure of the liquid in the conduit is. Accordingly also the position of the slide n with its pivot to is changed and thereon depends the extent of the pressure stroke of the pistons d. The latter suck the driving a medium through the. suction channels 7, from the conduit 7; and from the receptacle k compress the same and force it through the pressure channels 9 andthe receptacle 71, into thepressure conduit is, from which it enters, in a Working condition, the rear wheel motors 0. As the runnlng resistance increases, the pressure in'the conduit is and in turn in the cylinder q increases whereby the piston g is moved forward and in turn the spindle 0 is turned by means of the toothed wheel 0, so that the slide n with the pivot 11, is displaced in such a manner that the workin stroke of the piston d? is diminished, w e the-speed of the motor :a remains the same. In case the running resistanceis decreased the same operations in a reversed-order occuri: If a quick braking of the gear be desired it is only necessaryto shut up the suction conduit '5 more. or less by operatingthe foot lever 26. If the speed of f the motor is reduced by any circumstances, 1 10 as for instance, when-running upon hills, the regulator moves 1n an lnward d1rect1on,1;

while the sleeve 18 under the influence of the" spring 20-moves forward. If prior to thisthe coupling memberw was in engagementwith the part '0, such engagement is released.

in that the coupling member w is pulled for ward by means of the regulator rods 14. At'

the same time the collar 13 and the lever 10,

.depress the coupling part 2, mounted-on the sleeve 2 so that it engages the toothed wheel 'y, causing-movementof the toothed wheel w by the intervention of the intermediary wheel a: to be transmitted to the toothed wheel '1) whereby the latter is driven in a direction opposite to the direction of rotation of the toothed wheel w. Consequently, the spindle u moves thesleeve 8, toward the the regulator 15, whereby 'the spring '1' is-released for a corresponding amount and, owing to the. overpressure of'the driving inedium at q, the spindle o, operated bythe toothed wheel 0, effects a movement of, the

slide n with its pivot n (Fig. 1 toward the. left), until thepressure in the conduit is "and the' pressure of the spring r are balanced.

again; It follows thatthe working stroke of the piston d is .diminished and the speedof the engine increases again. With the. in

creasing speed of the engine athe regulator-rods 14 are pressed'rearwardly'by means of the correspondingly.revolving governor 15 and, as soon as the normal. speed is attained the toothed wheelszand 3 are disengaged.

Should it occur that the sleeve 8 is so excessively moved that it strikes against the coupling-member'v, the lever 5 may disengage the coupling-member y from the toothed wheel 2. The sleeve will in this case strike the loosely mounted grooved 001- lar- 8, move the same in forward direction I and thereby efiect a pulling back of the ton q is moved backward until the power is compensated. By means of the rack 72 the toothed wheel 0 is revolved and thereby "is and cylinder q will increase the s1 ide-,-;n' with; 151i; pivot a awed tut: wardly so that owing :to' the" greater eccen};

tricity the'stroke jof the-pistons d, and'in turn thework to be done by themotor' is atel and thus ;'compensate for the tension of the spring 1* and" thus the power stroke of the pistons d jtdconform to the desiredrate' of flow of the -liquid 8. i 'to the motors 0.

.' In Fig. 2- a form of embodiment is shown according to which instead oflthe spring "1 (Fig. -1) a pressure-'air cylinder ,Z is provided, the piston Q, of which is'rigidly connected to the piston q (Fig.1). The spring F of the regulator R is located in'thehollow'shaft The tension of. the spring F may beregulatedbymeanspf the rod D operatively connected with thecontroller for the gas-supply, or the ignition, thus varying the spring resistanceto the movement of the governor balls, in accord with the speed. for which the engine may be set.

The ,regulator R acts uponthe pressure -in. the' cylinder Zby reversing the valves V and V by means or cams N.

' When the engine is idling, the valve, V

is fully opened thus relieving the pressure in the pump P. With a working engine speed, however, the valve V closes and the valve Y opens, causing air to be forced under pressure into the cylinder Z with a resultant 1 increase in the effective stroke of the pistons d. With a decrease in the engine speed. the valve V is opened by the governor, R,- relieving the pressure in the' cylinder Z through said valve. both valves V'V being partly opened during "the change from one speed. to the other.

It is evident that a change for establishing 'a compensation between the runnlng resistance and the driving power takes place, as far as possible retaining the normal number of rotations of the motor.

I claim as my invention 1. 'A gear for attainingcompensation between driving power and load embodying therein in combination with an engine, a hydraulic pump drlve'n by said engine, a

hydraulic motor, pipes between the inlet and the exhaust of said motor and the pressure side and the suction side of said pump forming a closed circulating system. means adapted to vary'th'e capacity of said pump inclependently of the power applied thereto by said engine, a mechanical regulator operatively connected with said engine and having a normal tendency to vary the capacity of said pump in accord with a varying enupon the hydraulic motor will vary the gine speed, operative connections between said regulator and said means, a fluid. pressure regulator operatively connected with the pipe leading from the pressure side of 5 said pump, and. operative connections between said fluid pressure regulator and said connections between said mechanical regulator and the means controlling the capacity of the pump whereby variance in'the load capacity of said pump without varying the load upon the engine.

2. A gear for attaining compensation between driving power and load embodying therein in combination with an engine, a

hydraulic pump driven by said engine, a hydraulic motor, pipes between the inlet and the exhaust of said motor and the pressure side and the suction side of said pump forming a closed circulating system, means adapted to vary the capacity of said pump .independently of the power applied thereto by said engine, a mechanical regulator operatively connected with said engine and having a normal tendency to vary the capacity of said pump in accord with a varying engine speed, a compressible member interposed between said regulator and said means, a fluid pressure regulator operatively connected with the pipe leading from the pressure side of "said pump, and operative connections between said fluid pressure regulator and saidco-nnections between said mechanical regulator and the means controlling the capacity of the pump whereby.

variance in the load upon the hydraulic motor will vary the. capacity of said pump 7 without varying the load upon the engine. 3. A gear forattaining compensation be- 40 tween driving power and load embodying ,therein in combination withanengine, a'

hydraulic pump driven by said engine, a hydraulic motor, pipes between the inlet r and the exhaust of said motor and the pressure side and the suction side of said pump engine speed, operative connections between said regulator and said means, a fluid pressure regulator operatively connected with the pipe leading from the pressure side'of.

said pump, operative connections between said fluid pressure'regulator and said connections between said mechanical. regulator the pump whereby variance in the load upon the hydraulicvmotor will vary the capacity of said pump without varying the load upon the engine, and manually operative means a whereby the volume offluid passing and the means controlling the capacity of V through said circulating system may be varied.

4. A gear for attaining compensation between driving power and load embodying therein in combination with an engine, a plurality of rotatable cylinders driven by said engine, a casing forming a pressure and a suction chamber communicating respectively with said cylinders, a hydraulic motor, pipes between the inlet and the exhaust of said motor and said pressure chamber and said suction chamber respectively, forming a closed circulating system, a piston mounted in each of, said cylinders, a traveler, a pivot thereon, a rotatable member mounted upon said pivot, piston rods connected with said ro-- tatable member and said pistons respec: tively, means whereby said traveler may be moved toward or from the axis of rotation of said cylinders to vary the effective stroke of said pistons, and the capacity of said cylinders, a mechanical regulator operatively connected with said engine and having a normal tendency to vary the capacity of said cylinders in accord with the varying engine speed, operative connections between said regulator and said means for moving said pivot, a fluid pressure regulator operatively connected with the pipe leading from said pressure chamber, and operative connections between said fluid pressure regulator and said connections between said mechanical regulator and the means for moving said traveler whereby variance in the load upon the hydraulic motor will vary the capacity of said cylinders without varying the load upon the engine.

5. A gear for attainingcompensation between driving power and load embodying therein in combination with an engine, a plurality of rotatable cylinders driven by said engine, a casing forming a pressure and a suction chamber communicating respectively with said cylinders, a hydraulic motor, pipes between, the inlet and the exhaust of said motor and said pressure chamberand said suction chamber respectively, forming a closed circulating system, a piston mounted in each of said cylinders, a trav-- eler, a pivot, a rotatable member mounted .upon said pivot, piston rods connected with said rotatable member and said pistons respectively, a rotatable shaft provided with a gear and means engaging said traveler whereby 'said traveler may be moved toward or from the axis of rotation of said 'cylins ders to vary theefli'ective stroke of said pistons and thecapacity of said cylinders, a. mechanical regulator ,operatively connected with said engine and having a normal tendency to vary the capacity of said cylinders in accord with a varying engine speed, a reciprocatory rack engaging said gear, aflexible connection between said rack and-said mechanical regulator, and a fluid pressure regulator operatively connected with the pipe leading from said pressure. chamber, and with said rack whereby variance in the load upon the hydraulic motor will vary the capacity of said cylinder without varying the load upon the engine.

SQA gear for attaining compensation'between driving power and load embodying therein in combination with .an, engine, a.

a gear and means engaging saidtraveler whereby said traveler may be movedtoward orfrom the axis of rotation of said cylin: ders to vary the effective stroke of said pistons and the capacity of said -cylinders,.a mechanical regulator operatively connected with said engine and having a normal tendency to vary the capacity of said cylinders in-accord with a varying engine speed, a reciprocatory rack engaging said gear, a flexible connection between said rack and said mechanical regulator, a fluid pressure regulator operatively connected withthe pipe leading from said pressure chamber and with said rack whereby variance in the load upon the hydraulic motor will vary'the capacity of said cylinder without varying the load upon the engine, and manually operative means whereby the volume .of fluid passing through said circulatingsystem may be varied.

7. A gearfor attaining compensation between driving power and load embodying therein in combination with an engine, a plurality of rotatable cylinders driven by said engine, a casing forming a pressureand a suction chamber communicating respectively with said cylinders, a hydraulic motor, pipes'between the inlet and the. ex-. haust of said motor and said pressure cham-- ber and said suction chamber respectively, forming a closed circulating system, a piston mounted in each of said cylinders, a traveler, a pivot thereon, a rotatable member mounted on said pivot, piston rod s-con-.

' nected with said rotatable member, a rotatable shaft provided with a gear and means engaging said traveler whereby said.

traveler may be moved toward or from the axis of rotation of said-cylinders to vary the effective strokeof said pistons and the capacity of said cylinders, a centrifugal governor driven from said engine, a reciproipes' between the inlet and the excatoryrack engaging said gear, a recipro-* catory' screw sleeve, a flexlble connection'between said sleeve and sa1d rack, a screw shaft coeperating with said sleeve, a clutch mechanism whereby said screw shaft -maybe operatively connected with said governor whereby there is a normal tendency to vary the capacity of said cylinders. in accord with a varying engine speed, anda fluid pressure regulator operatively connected with the pipe leading from said pressure chamber load upon the hydraulic motor will vary the capacity of said cylinder without varying 'the'load upon the engine, and manually operative means whereby the volume of fluid passing through said circulating system may be varied.

8. A gear for attaining compensation between driving power andload embodying. therein. in combination with an engine, .a pluralityv of rotatable cylinders driven by said engine, a casing forming a pressure and and with -said rack whereby variance in the.

a suction chamber communicating respec-.

tively with said cylinders, a hydraulic motor, pipesbetween the inlet and the exhaust of said motor and said pressure chamber and said suction chamber respectively, forminga closed circulating system, a piston mounted in each of said'cylinders, a traveler, a pivot thereon, a rotatable member mounted. on. said pivot, piston rods onnected with said rotatable member, arotatable shaft provided with a ear and means engaging sa1d traveler where y said traveler may be moved toward-or from the axis of rotation of saidcylinders to vary the effective stroke of said pistons and the capaclty of said cylinders, a centrifugal governor driven from said engine, a reciprocatory rack engaging said gear, a reciprocatory screw. sleeve, a. flexible connection between said sleeve and said rack, a screw shaft cooperating-with said sleeve, a clutch mecha nism whereby said screw shaft may be'operatively connected with said governor whereby there is a normal tendency to vary the capacityof said cylinders in accord with a varying enginespeed, gears carried by the cofiperatmg members of said clutch mechanism, a gear tram connecting said gears, a

train may be actuated to reverse the movement of said sleeve, actuating means for said second clutch in operative connection with said governor, and a fluid pressure regulator second clutch mechanism whereby. said gear operatively connected with the pipe leading from said pressure chamber and with said rack whereby variance in theload upon the hydraulic motor will vary the capacity of said cylinder without varying the load upon the engine, and manually operative means whereby the volume of fluid passing through I *said circulating system may be varied.-

9. A gear for attaining compensation betor, pipes between the inlet and the exhaust of said motor and said pressure chamber and said suction chamber respectively, formi ing a closed circulating system, a piston mounted in each of said cylinders, a traveler, a pivot thereon, a rotatable member mounted on said pivot, piston rods connect 1 ed with said rotatable member-,a rotatable shaft provided with a gear and means engaging said traveler whereby said traveler may be moved toward or from the; axis of rotation of said. cylinders to vary. the efiective stroke of said pistons and the capacity of said cylinders, a centrifugal governor driven from said engine, a reciprocatory rack engaging said gear, a reciprocatory' screw sleeve, a flexible connection between said sleeve and said rack, a screw shaft co operating with said sleeve, a clutch mechanism whereby saidscrew shaft may be operatively connected with said governor whereby there is a normal tendency to vary the capacity of said cylinders in accord with a varying engine speed, gears carried by the cooperating members of said clutch mecha-.

nism, a gear train connecting said gears, a second clutch mechanism whereby said gear train maybe actuated to reverse-the movement of said sleeve, actuating means for said second clutch in operative connection with said governor, means adapted to be actuated by said sleeve to automatically release said- 7 1 second clutch, and a fluid pressure regulator operatively connected with the pipe leading from said pressure chamber and with said hydraulic pump driven byfisaid engine plurality of hydraulic motors operativel connected respectively with two'independ ently' movable load sustaining membe pipes between the pressure and'the su'cti'oir rack'where'by variance in the load upgm the v hydraulic motor will vary the capacity of said cylinder without varying the load upon the engine, and manually operative 1neansj4$ therein in combination with anjeng'ind '1 sides of said pump and'the inlet and the,

' exhaust of one of said motors,br.anch pipes leading from said first named pipes to the inlet and the exhaust of said other motor whereby a closed circulating system including both said motors is formed, means adapted to vary the capacity of said pump independently of the power applied thereto by said engine, a vmechanical regulator operatively connected with said engine and hav: ing 'a normal tendency to vary the capacity of said pump in accord with a varying env gine speed, a fluid pressure regulator opel'utivelytconnected with the pipe leading from the pressure side of said pump, and operative connections between said mechanical regulator and the '.'means controlling the capacity of the pump whereby variance in the load upon the hydraulic motor will "vary the capacity of said pump without varying .the load upon the engine.

' In testimony whereof I afiix my signature v inthe presence of two witnesses. GEORG VON SAALFELI).

. Witnesses: U; Runner,

ARTHUR G-UBE. 

